Shock absorber



April 4, 1939.

H. JoH'ANsEN sHocK ABSORBER Filed Jan. 28, 1958 2 Sheets-Sheet l H. JoHANsEN 2,152,740

SHOCK ABSQRBER Filed Jan. 28, 1938 2' Sheets-Sheet 2 April 4, 1939.

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Patented Apr. 4, 1939 UNITED STATES PATE NT OFFICE Y 2,152,746 v SHOCK .LxBsoRBERgl y Hans Johansen, Mantua, Ohio Application January 2s, 193s, strain?, 187,422`

11 claims.

This invention relates to a shock absorber for vehicles and the like which is suitable for use in connection with automobiles Where the body is resiliently mounted on a support and forces of impact or shock are transferred to the body from the-supportresulting in objectionable oscillations of the body on the support. This shock absorber is equally useful in connection with the drawing of heavy transitory equipment, such as railway cars, where heavy shocks Aare imposed on the coupler connecting the heavy equipment to their source of locomotion, and also where shocks are imposed during the actual transitory movement of the equipment, which shocks, so imposed on the coupling member, are substantially transferred therefrom to the body and cause considerable damage to the body and also a great loss of power. The use of this shock absorber is practical and effective for damping gun re shocks produced in the use of artillery equipment, and it is recognized that many other uses may be made for effectively damping heavy shocks.

It is a principal object of this invention to provide a two-way, double-cycle, shock absorbing means which is effective for damping shocks in either of two directions, as when the absorber is used in connection with a coupling member of a heavy transitory body or inrconnection with a resiliently supported vehicle body. In my Patent No. 2,023,527 issued December 10, 1935, there is described a coupling member which is basically a shock absorber and is effective in damping such shocks as heretofore described, and the present invention is directed to an improvement thereof,

' especially in securing an increased damping effect of the shocks for the purpose of substantially preventing these shocks from being transferred to the vehicle body or frame.

It is an important object of tl'lisY invention-to provide a two-Way shock absorbing means for damping shocks accompanying the application of a force to a body by gradually making application of the force to the body until a complete application is made, and upon decrease in magnitude of the force applied to the body, or upon a force being exerted in the opposite direction tok thatof the first applied force, making a gradual application to the body of the variation of magnitude or reversal in direction for damping the shock.

It is an equally important object of this invention to provide a two-way shock absorbing means for acoupling member for use on a heavy transitory body which has a member movable relative to the body and resisted in movementv by fluid,

Whichsholg absorbing means causes a force applied to the movable member to be graduallyV transferred to the heavy body.,an,d upon substantiallyftransferring the forcesto the body,K4 continuing such transfer through the fluid resistance during the` continuance of the application. of force to the member, whereby the force is applied to thebody without substantial impact or shock.

It is a more specicZ object of this invention to provide a two-way shock absorlcyingY means, for a coupling member for use on a yheavy transitory body which,A has a member movable `relative to the body, which means is operative for resisting by Viiuid pressureA the movement of the member upon application of a force to theY member and includes means forV producing a maximum relief to the fluid resistance caused by the initial movement o f the movable member and for gradually decreasing the relief during continued movement untila maximum resistance is` produced, whereby the shocklof force applied to the movable member is damped and the subsequent continued applied force is entirely transferred gradually through the fluid resistance to the body until all the applied force is effective on the body.

Ity is a further object of this invention to pro-v vide for use on a heavy transitory body having a coupling. member movable relative to the body and resistedk by fluid, a means for relieving the fluid resistance produced upon the initial movementvof the member by a force applied to the member, and for gradually reducing the relief to the resistance during vcontinued movement of the member. in the same direction until a maximum resistance is produced, whereupon the force acting on the movable member is transferred to the body through the fluid resistance produced, and saidmeans damping shocks imposed upon the movable-member during the application and continuance of application of the force through the fluid resistance to the body.

v It is a correlative object of this invention to provide a-two-way shock absorbing means for a resiliently supportedy body having a member movable relativeV to-v the body and resisted in movement by fluid, means for relieving fluid resistance upon. initial movement of the member from a normal position and for gradually decreasing such relief during continued movement of thev memberV inthe same direction until av maximum resistance is produced and continuing such resistance during continued movement of the member in the same, direction and gradually increasing the reliefV during the return ofthe member to its ynorrial position.

l accompanying the application of force to the body are appreciably damped are adaptable also in effecting the damping of the shocks received by the axle of a self-propelled vehicle.

In the drawings, Fig. 1 is a sectional view illustrating an embodiment of my invention;

Fig. 2 is a partial sectional view illustrating the same embodiment in one operative position;

Fig. 3 is a partial sectional View illustrating the same embodiment in another operative position;

Fig. 4 is a transverse sectional view along the line 4--4 of Fig. 1;

Figs. 5, 6 and 7 are plan, side and end views, respectively, of the valve plate illustrated in Fig. 1;

Fig. 8 is a plan view, and Fig. 9 is a sectional view along the line 9-9 of Fig. 8, of a plunger element illustrated in Fig. 1;

Fig. 10 is an illustration of another embodiment of my invention;

Figs. ll and 12 are fragmentary longitudinal sectional views, each illustrating an operative position of thisV embodiment;

Fig. 13 is a fragmentary transverse section taken along the line I3-I3 of Fig. 10;

Figs. 14, 15 and 16 are side, plan and end views, respectively, of a spindle valve illustrated in the embodiment of Fig. 10.

In the general assembly of a shock absorber, especially of the piston type, the outer housing or cylinder is connected to the frame or body,

and the relatively movable member or piston is arranged for connection to the coupler, in the case of a drawn vehicle, or to the axle, in the case of a self-propelled vehicle.

In Fig. 1, the housing or outer cylinder I is arranged for yconnection to the frame of a vehicle (not shown), and the piston 2 is arranged for connection to a coupler or axle (not shown).

A working yfluid chamber 9 is defined by an inner surface of the cylinder I, an outer surface of the piston 2, and a pair of oppositely disposed shoulders 6 and 'l on the piston 2 and shoulders 4 and 5 on the cylinder I. For the purpose of assembly, the shoulder 6 on the piston is formedV by means of a sleeve 8 threaded to the piston 2 and the shoulder portion 5 of the outer cylinder is formed by an inner gland plate I| threaded to the cylinder I. The working chamber 9 is thus formed between the surfaces of the cylinder I and piston 2 and limited and defined in its length by the shoulders 4 and 5 of the cylinder I and shoulders 6 and of the piston 2. The piston 2 is supported by the sleeve 8 acting against an inside-surface of the cylinder I and also by a gland member I which is composed of the inner plate II and a pressure member I2 which is likewise threaded to the cylinder I and exerts a pressure against the gland material I3 for forming a pressure-tight joint between the surfaces of the gland l0 and the supported surface of the piston 2.

A plunger I4, as illustrated in Figs. 8 and 9, is normally positioned in the working chamber 9 against the shoulders 4 and 6 of the cylinder I and piston 2, respectively, by a spring I5. A like plunger I6 is positioned against the shoulders 5 and 'l of the cylinder I and piston 2, respectively,

by the same spring I5. Fluid is entrained between Y the operating faces of the plungers I4 and I5 which are so arranged that movement of the piston 2 in one direction, for example, relatively Y downwardly in Fig. 3, causes the shoulder 6 to move the plunger I4 into the working chamber 9 while the plunger Iis held in position by the shoulder of the cylinder I, and movement of the piston 2 in the opposite direction, for example, relatively upwardly in Fig. 2, causes the shoulder 'I to move the plunger I6 into the compression chamber 9 While the plunger I4 is held in vposition by the shoulder 4 of the cylinder I.

For the purpose of relieving the pressure or fluid resistance developed in the working chamber 9 by the relative movement of the plunger elements I4 and I 6 toward each other, relief is given to resistance in a manner so that an effective damping action can be secured for the purpose of preventing the objectionable shocks or impacts received by the piston`2 being transferred to the cylinder I and thence to the` frame or body of the vehicle to which the cylinderk is connected. Fig. 1 illustrates a means embodying the invention and which provides this manner of relief of fluid resistance produced when the piston 2 is moved from the indicated normal' position-of Fig. 1. In this embodiment, referring to Figs. 1 to 9, inclusive, relief is secured by the openings 20 and 2| ofthe plunger I4, and like openings 22 and 23 of the plunger I6. In other words, because of the presence of these openings in the plungers I4 and I6, the pressure or fluid resistance is relieved upon the initial movement of the piston 2 in either of the two directions, whereupon, if a moving force be applied to the connectible end 25 of the piston 2, very little, if any, resistance would be produced by the action of the plunger elements I4 and I6 as they are ings 23 of plunger I5 into the formed relief cham- Y ber 3|, while, if vthe piston 2 is moved in the opposite direction, as indicated in Fig. 3, from the normal position indicated in Fig. 1, the fluid resistance would be relievedthrough the openings 2| of plunger I 4 into the formed relief chamber 32, and through the openings 22 of plunger I6 into the formed relief chamber 33, as illustrated in Fig. 3. For the purpose of securing afbalanced relief action on the piston 2, a pair of openings 20 and 2| are placed in the plunger I4, Figs. 8 and 9, and a pair of openings 22 and 23 are placed in the plunger I6 in a similar manner. However, a single opening 20 may be placed diametrically opposite a single opening 2|, and likewise a single opening 22 may be placed diametrically opposite a single opening 23 for providing an operative structure.

In the embodiment of my invention illustrated in Fig. 1, a valve plate 46 may be aliixed to the surface of the cylinder I by a slot and screw arrangement, as illustrated in Figs. 1 and 4, and a valve plate 4l to a surface of the piston 2 by a similar arrangement for cooperating with the valve surfaces 48 and 49 on the plunger I4, and valvesurfaces 50 and V5I on the plunger I6. Likewise, valve plates 40 and 4| are affixed to the surfaces of the cylinderl and 'piston 2, re- 75 spectively, and cooperate with valve surfaces 42 and 43 of the plunger I4, and valve surfaces 44 and 45 of the plunger I6, respectively. Figs. 5, 6 and 7 show in detail a construction of valve plate illustrated in Fig. 1. These valve plates consist principally of a base surface 60 having valve surfaces consisting of diverging surfaces 6| and 62 which are terminated by cut-offs 63 and 64, and continuing with a pair of diverging surfaces 6 5 and 66 which terminate in a flat surface 61. The presence of these cut-offs 63 and 64 is not necessary on the valve plate since the embodiment will operate effectively if diverging surfaces 6| and 62 are terminated by the flat surface 61.

It is to be observed that although in Fig. l there Vare illustrated two sets of valve plates 40 and 4| and 46 and 41, the absorber may be made with one set of valve plates, as plates 46 and 41, controllingl the relief of the fluid resistance to the formed relief chambers, such as 30 and 3| in Fig. 2, and 32 and 33, in Fig. 3. Also, the plates need not be positioned as illustrated in Figs. 2 andv 3 in that plate 46 may be positioned anywhere on the surface of the cylinder I and plate 41 anywhere on the surface of the piston 2. As an example, valve plate 4|) may be used in conjunction with valve plate 41, and also valve plate 46 may be used in conjunction with valve plate 4|. It is necessary that some valve means be provided for controlling the relief from the working chamber 9 to the formed relief chambers 36 and 3|, Fig. 2, and also the control of the relief from the working chamber 8 to the formed relief chambers 32 and 33, Fig. 3.

In the operation of the embodiment illustrated in Fig. 1, upon the application of a pulling force to the piston 2 in a direction such that the piston is moved outwardly, as illustrated in Fig. 3, the shoulder 6 on the piston 2 causes a movement of the plunger I 4 into the Working chamber 9 against the action of the spring I5 and against the resistance of the fluid in the Working chamber 9. At the same time, the plunger I6 is held against the shoulder 5 of the cylinder by the action of the fluid pressure produced by the movement of the plunger I4 and also by the action of the spring I5. By the movement of the plunger I4, a relief chamber 32 is produced, and upon movement of the piston 2, as illustrated in Fig. 3, a relief chamber 33 is produced. At the instant of relative movement of the piston 2, the resultant openings 2| are limited by the valve plates 46 and 40 and the resultant openings 22 of plunger I6 as limited by the valve plates 41 and 4| of the plunger I4 substantially completely relieve the fluid resistance produced at the instant of initial movement. Upon further movement in the same direction, the action of the diverging surface 6I of the valve plates 4D and 46 acting in cooperation with valve surfaces 42 and 48 of the plunger I4 cause a reduction in the amount of the opening 2| in a manner such that upon continued movement of the plunger I4 in the same direction as the initial movement, the relief of the fluid resistance to the relief chamber 32 is gradually reduced until the plunger element I4 reaches the position illustrated in Fig. 3. Continued movement of the plunger I4 in the same direction causes an instantaneous substantial relief of the pressure because of the cut-off 63 of valve plates 46 and 46, but upon continued movement the relief is gradually decreased, due to the diverging surface 6,5 of valve plate 4,6 and 46 which terminates in a fiat surface 61 of each of the valve plates, at which time the maximum fluid resistance is produced. During movement of the plunger I4 as above described, the plunger I6 is held in position by shoulder 5 of cylinder I, but the movement of the piston 2 and valve plates 41 and 4 I, cooperating with the valve surfaces 5| and 45 of plunger I6 similarly reduces the relief of the fluid resistance by the passing of fluid from the working chamber 9 to the formed relief chamber 33. The effect of this action of gradual decrease in the relief tothe resistance produces a damping action to shocks which are received by the piston 2, and because of this damping action, the shocks are eliminated or substantially decreased and not transferred to the cylinderjl and thence to the body of the vehicle.

Upon return of the piston 2 to its normal position, a gradual increase in relief is produced until a maximum relief is provided', at which time the piston will be at or near its normal position. Continued movement of the piston 2 in the same direction produces conditions as set forth in connection with the description of4 Fig. 2.

A force or shock being applied to the piston 2 in a direction opposite to that described inconnection with Fig. 3 causes a relative movement of the piston 2, as illustrated in Fig. 2. Upon such relative movement, the relief chambers 30 and 3| are formed consequent upon the movement of the piston 2. Due to the diverging surfaces 6I of valve plates 4| and 41 and surfaces 62 of valve plates 40 and 46, the iiuid resistance produced by the initial movement of the plunger element I6 is substantially completely relieved through the resultant openings formed by the openings 26 of the plunger I4 and the valve plates 4| and 41 of the piston 2 to the formed relief chamber 30, and the resultant openings in the plunger I6 formed by the openings 23k and the valve plates 46 and 46 of the cylinder I to the formed relief chamber 3|. This relief is gradually decreased during continued movement in the same direction of the piston 2 by the cooperative action of valve surfaces 43 and 49 of the plunger I4 with surfaces on the valve plates 4I and 41, respectively, controlling the fluid relief to the chamber 36, and likewise valve surfaces 44 and 5I) of plunger I6 cooperating with surfaces on the valve plates 40 and 46, respectively, in controlling the fluid relief to the chamber 3| until the plunger elements reach the position illustrated in Fig. 2. At this time, because of the cut-offs 63 on the surfaces of the valve plates, a substantial instantaneous relief is produced upon further movement of the piston in the same direction. This action is followed by a gradual decrease of the relief of the resistance upon continued movement in the same direction as illustrated in Fig. 2 until a maximum resistance is produced, at which time the valve surfaces of the plunger elements I4 and I6 will contact the flat surface 61 of the valve plates.

During such action of relief of the resistance, the shock received by the piston 2, causing relative movement of the piston, is substantially clamped, and ther shock is not transferred t o the cylinder I, and thence to the frame or body of the vehicle.

Upon the return of the piston 2 to its normal position, as illustrated in Fig. 1, from its eX- treme displaced positions in the directions of movement as illustrated in Figs. 2 and 3, a further damping action is produced in the gradual increase of relief of fluid resistance produced, in the relief chambers, which resistance opposes the movement of the pistonZ b ackto'v its, normal` position. This gradual increase in relief is secured by theA cooperative action of the valve surfaces on the plungers with the valve surfaces on the-valve plates, so thatr the relief to the fluid resistance is very small at the instant of movement of the piston 2 back to its normal position.

As the piston 2 continuesY its movement in the l same directiontoward its normal position, the relief is gradually increased until a substantially complete relief is produced, at which time the piston is at. or near its normal position, as illustrated in Fig. 1.

In the use of this embodiment of my invention as a shock absorbing means for a coupling mem.- ber on a relatively heavy transitory body, a Vforce being applied to the coupler is transferred to the body in a manner so that the eifect of the impact or shock accompanying such application of a force to the body is substantially decreased or eliminated. y Continued application of the force in the same direction as would ordinarily occur in moving the body from one location to another is made to the body through the fluid resistance set up by the displacement of the members, as illustrated in Figs. 2 and 3. Should leakage dissipate the uid resistance created, the complete load or force supplied to the coupler is then transferred to the body through the spring |5.

Upon the application of a force in a direction opposite to theV force which has caused the displacement of the members resulting in a maximum resistance, this force in the opposite direction would be-applied to the body in a manner such that the Yshock or impact accompanying the application of such reversal in direction of force is substantially or rentirely eliminated. If the force is continued in this same reverse or opposite direction, it is gradually applied to thebody upon the movement of the piston 2, from the normal position, as illustrated in Fig. 1, to a maximum distorted position, as heretofore described in connection with Figs. 2 and 3, whereupon the force is applied to the frame or body through the created fluid resistance or through the spring.

Additional shocking means may be provided by the employment of a cylinder 11, Fig. 1, which is formed within the piston 2 and having a movable piston 16 working within the cylinder 11 and resisted in movement by a spring 18 and connectible by a passage 15 formed by an inner surface of cylinder and an end surface of piston 2. Upon the movement of the piston 2 into'the chamber 90, fluid pressure is produced by the fluid entrained therein, causing the uid to pass through the passageway 15 to a surface 92 of the piston 16, thereby causing the piston 16 to move into the cylinder 11 and against the spring 18. For resisting the movement of the piston 16, iiuid is placed in the cylinder 11 which resists the action of the fluid acting against the surface 92 of the piston 16 from the passage 15. In order that the fluid pressure produced on the side 9| of the piston may be relieved, a by-pass 19 is provided having small passageways 80all being formed in the piston 2. These small passageways 88 may be connected to the cylinder 11 at distances as illustrated, this location of passageways 80 depending upon the extent-of relief necessary for the proper operation of the cushion.- ing or dampening of the piston 2 as it moves into the chamber 90. This additional shocking means is useful especially when used in connection with a coupling member of a heavy body.

Many modifications incorporating inve'ti'ri may be made over that illustrated in Fig. 1 which would produce similar or like results in the Veflectivedamping action. ne such modication is illustrated in Fig. 10. In this embodiment there has been substituted for the stationary valve plates. 40 and 46 needle or spindle valves and |56, respectively. This type of valve is shown' in detail in Fig. 16, and consists of a body ||5 having a pairA of diverging surfaces |04 and |05 which are interrupted by a cut-01T |06 and |01, followed by a continued pair of diverging surfaces4 |08 and |09. The spindle valve is made up of a pair of these valve bodies 5 connected together by being threaded to the same shaft A separable valve element 200 is placed adjacent each of the valve bodies'il5 and it is held againstthe valve body by a spring |59, as in Figs. 10, 11 and 12.

In the embodiment illustrated in Fig. 10, many Vof the principal parts of the absorber'are similar to those illustrated in Fig. V1, and a description of these parts will not be given in detail because of such similarity. The piston |20 fits` into the hollow cylinder |2|, and the cooperating shoulder elements |22 and |24,and` |23 and |25 of the piston |20-and the cylinder |2|, respectively, and surfaces of the piston and cylinder form a working chamber |26. The shoulder |22 is formed by a sleeve |30 threaded to an end of the piston |20, and the shoulder |25 of the cylinder'is formed by a gland |21 threaded to the cylinder |2 The plunger elements |32' and |33 are positioned against the shoulder elements of the piston and cylinder by a spring |36. Openings are formed in the plunger elements for the purpose of relieving the fluid resistance produced during movement of the plunger elements into the working chamber |26. 'Such openings are shown at |40, |4|, |42 and |43 of the plunger element |32, and at |44, |45, |46 and |41of plunger velements |33, Figs. 10, 11 and 12'. Cooperating with openings |4| and |45 is a stationary'valve plate |50,

and cooperating with openings |40 and |44 is a spindle valve |5|. Likewise, cooperating with openings |42 and |46 is a stationary Valve plate |55, and cooperating with the openings |43 and |41 is a spindle valve |56. Fig. 13 illustrates this cooperation of the spindle valve and the stationary plate |55 with the plungers |32 and |33. .Y There is also illustrated the cushioning device formed by the compression of fluid in the chamber |10 upon movement of the piston |20. 'I'he -cushioning is further accelerated by a cylinder |80 in the piston having a piston 8| and resisted in movement by fluid and by a spring |82, lthe cylinder |80 being connected to the chamber' |10 by a passage |85.' The by-pass |86 is formed in the piston |20 having passages |81 for relieving the fluid pressure exerted upon the move-ment of the piston |8| into the cylinder |80. As the piston |20 is moved into the chamber |10, fluid pressure in the chamber |10 opposes this movement, which is gradually relieved by the movement ofthe piston |8| relative to the cylinder |80.

As the piston |8| moves relative to the cylinder |80, the pressure resisting its movement use of my shock absorbing means with a coupler since shocks of great intensity are applied to the coupler in a direction causing movement as illustrated in Fig. 12.

In the operation of the embodiment illustrated in Fig. 10, upon a shock being received bythe piston |20, resulting in relative movement of the piston with respect to the cylinder 2| as illustrated in Fig. 11, this movement causes relative movement of the plunger element |32y into the working chamber |26, which movement is resisted by uid and by the spring |36. The fluid resistance is relieved by the openings connecting the Working chamber |26 with the formed relief chambers, hereinafter described. The openings in the plunger element resulting from the cooperation of the valve members and the plunger elements are of sufficient size to substantially completely relieve the fluid resistance produced consequent upon initial movementof the plunger elements |32 and |33 into the working chamber |26.

By the relative movement of the piston |20 from the normal position as illustrated in Fig. 10, and assuming a shock or impact is received by the piston member |20, causing its movement as illustrated in Fig: 11, the relief of the resistance is substantially completely relieved through openings |40 and |43 in plunger |32 to the formed relief chamber |90, and openings |45 and |46 in plunger 33 to relief chamber |9|. and the relief is gradually reduced through the openings |40 and |43 to the relief chamber |90 by the action of the valve surfaces of the plunger |32 cooperating with the valve surfaces ||04 and |05, Figs. 14, 15 and 16, of the spindle valves |5| and |56, and the relief through the openings |45 and |46 to the relief chamber |'9I` is gradually reduced by the action of valve surfaces on the plunger |33 and on the valve plates |50 and |55, until the plunger reaches the position illustrated in Fig. 11.

Upon further movement in the same direction of the plunger |32 into the Working chamber |26, an instantaneous relief is produced by the cutoifs |06 and |01 of spindle valves |5| andA |56, followed by a gradual decrease in the relief by the action of the valve surfaces of the plunger |32 cooperating with the diverging surfaces |08 and |09 of the spindle valves |5| and |56 and valve surfaces of plunger |33 and cooperating surfaces of valve plates |50 and |55 until a maximum resistance is produced, at which time the plunger |32 engages the valve elements 200 of spindle valves |5| and |56, closing openings |40 and |43, and the openings |45 and |46 have been closed by surfaces of the valve plates |50 and |55, which completely cuts off any further relief except that which is produced by leakage. Upon further movement of the plunger |32 in the same direction as illustrated in Fig. 11, the action is resisted by the spring |59 which normally positions the valve elements 200 against surfaces of the pair of valve bodies ||5. By this manner of decrease of relief of the resistance, the shock received by the piston |20 resulting in its relative movement is appreciably damped, thereby preventing its transfer to the cylinder |2|. A further damping action is secured upon the return of the piston |20 to itsi normal position in a direction of movement as illustrated in Fig. 12, in that the relief of the fluid resistance produced is gradually increased until a full relief is secured. If the movement of the piston |20 continues beyond its normal position, as illustrated in Fig. 10, in a direction as illustrated in Fig. 12, the fluid resistance produced consequent upon this further movement will be gradually decreased in relief in a like manner, that is, the fluid resistance produced by the movement of the plunger element |33 into the working chamber |26 is relieved through the openings of the plunger elements |32` and |33, respectively, as illustrated in Fig. 12.

VvBy the action of the cooperating valve surfaces of the spindle valves |5| and |56 with the valve surfaces` of the plunger element |33, 'the relief of the resistance to the formed lrelief chamber 2|0. is gradually reduced, and likewise the relief of the resistance to the formed relief chamber2| is gradually reduced by the action of the valve surfaces of the plunger element |32 cooperating with the stationary valve plate |50 andl |55. This gradual decrease in relief continues until the plunger element |32 reaches th'e cut-offs |06 and |01 of the spindle valves |5| and |56, resulting in a substantially instantaneous decrease in relief of the fluid resistance, followed by a gradual decrease in relief upon further movement of the plunger element |33 into the working chamber 26 until a position is reached as illustrated in Fig. 12, at which time, upc-n further movement of the plunger element |33, any relief to the uid resistance would be secured by means of leakage. At this time, the plunger element |32 has reached the position illustrated in Fig. 12, whereupon the relief of fluid resistance to the relief chamber 2| I is substantially cut off except as secured by means of leakage. The piston |20 starts from its normal position as illustrated in Fig. 10 and moves in the direction indicated in Fig. 12, whereupon a damping action is produced similar to that produced when the piston moves in the direction illustrated in Fig. 11.

An advantage of the use of a positive action type of valve as the spindle valve |56 is in the use of my shock absorbing means in connection with a coupling member for heavy bodies; that is, when the piston |20 has moved to a position as indicated in Fig. 12, the force acting on the piston is then completely transferred to the body through the fluid resistance and the cylinder I2 By a positive type of valve, leakage is eliminated and the fluid resistance can be maintained for transferring force therethrough. Such type of valve can be substituted for the valve plates 50 and |55. Should the fluid resistance be relieved by leakage, then the force is transferred to the body through the spring |36.

Modifications may be made of the valve arrangement over that illustrated in Fig. 10, as in the use of a single stationaryvalve plate |55 and a single valve spindle |56 for producing an effective damping action of shock received by the piston |20. The advantage in the use of the arrangement illustrated in Fig. 10 is that it produces a balanced damping action upon movement of the piston 20. It is possible to position the spindle valve |56, as illustrated in Fig. 10, and then to use a stationary valve plate |50, Fig. 10, which is diametrically opposite lin location from the valve spindle |56. This arrangement provides an effective damping action and also a more balanced condition than an arrangement of placing the spindle valve and the valve plate side by side, but the effectiveness in damping is less than that of the modification illustrated in Fig. l0. In the use of either of the embodiments illustrated in Fig. 1 or Fig. 10, the effectiveness of the cushioning chambers and |10 of Figs. 1 and 10, respectively, is greatly increased when used in connection with a coupling member for a drawn body; that is, the tremendous shocks imposed upon the coupling member and directly transferred to the shock absorbing mea-ns are eifectivelyrdampened by the gradual decreaseof the relief of the cushion produced upon the movement of thepi'ston |20 into the chamber H0 of Fig. 10, and likewise the movement of the piston V2 into Vthe chamber 90 of Fig. 1. Y

Generally, my vinvention provides a shook yabsorbing means having a movable memberl relative to a body and which is resisted in movement in either of two directions in such a manner that upon initial movement of the member from'a normal position caused by the application of a force in one ofthe two directions, theuid resistance is substantially relievedand upon continued movement. in the same one ofthe directions, the relief is gradually decreased until a maximum resistance is produced, at which time the force then acting on the member and in the same one direction is transferred to theY bodyby the resistance, or ifthe force s consists of a substantially instantaneous shock desired to be completely damped, the manner of relief of resistance substantially damps and prevents the shock from being transferred tothe body. Return of the movable member from a dis- Y torted position to its normal position produces a damping effect by the gradual increase in the relief of the resistance until the member reaches its, normal position. Upon vcontinued movement of the member in the same direction beyond the normal position by reason of a continued application of the force in the same direction, such'force is applied in a gradual manner to the body because of rthe gradual decrease in the relief Yoi the fluid resistance until a maximum l,resistance is produced, at which time the force acting in the opposite, direction .is completely transferred to the body. y y Y YIt is to be understood that although the invention has been described in some instances in connection with the continued application ,of forces to a body, as would occur in the use of the shock v absorbing means in connection with'acoupling member, the invention is not to be limited thereby since it has wide application, as in the caseof a resiliently mounted body where it is desired to prevent or substantially decrease any transfer of force from the support to the, body, and therforce so applied to the support is not of a continuing nature but is generally of anV instantaneous nature, as in the case where the support strikesjan obstruction, causing movement of the support relative to the body, and it is desired to prevent this transfer to the body of movement or shock.

.Having thus describedrmy inventionfI claim:

1. In a two-way shock absorber means including a hollow cylindrical member having a nrelatively movable member telescopically mounted therein andV a iluid chamber formed bysurfaces of the members, end limitsof the .fluid chamber being defined by cooperating shoulder portions onYV each of the members, displacement means disposed at each end of the chamber and held in anormal position vagainst the shoulder portions by a yieldable means for forming a working chamber, fluid in said working chamber for resisting movement of said relatively movable member, and comprising openings in said displacement Vmeans for relieving fluid resistance produced by movement of said movable member in either of the two direc- Y tions of movement, and valvemeans in said openings operable by the movement of the relatively movable member in either ofthe two directions for gradually reducing the relief in the resistance produced consequent upon movement of the relatively movable member in either of the twov directions from its normal position until a maximum resistance ls produced, and for gradually relieving the maximum resistance produced during the return ofthe movable member to its normal position. Y

2; In a two-way shock absorber means including ahollow cylindrical member having a relatively movable cylindrical member telescopically mounted therein and a fluid chamber formed by surfaces of the members, end limits of the-fluid chamberbeing dened by cooperating shoulder portions'on each of the relatively movable memr bers, displacement means disposed at each end ofk the chamber and held in anormal Yposition'agai'nst the shoulder portions by a yieldable meansv for forming a working chamber, fluid in said working chamber for resisting movement of said relatively movable member, andV comprising openingsin said displacement means for relieving fluid resistance produced by movement of said movable member in either of the two directions of movement, and

'valve means in said openingsv operable by the -movement in either of the two directions of the relatively movable member, said valve means gradually decreasing the relief of the fluid resistance until a predetermined resistance is produced upon movement from va normal position Yof' said movable member in either of the two directions, instantly substantially relieving the iiuid resistance upon further movement of the member in the same direction and gradually decreasing the relief during continued movement in the same directionuntil a maximum iiuid resistance is pro duced.

3. In a two-way shock absorber including a hollow cylindrical member having internally spaced oppositely disposed shoulder portions, a relatively movable member telescopically mounted within the hollow member and having oppositely disposed shoulder portionsV which. cooperate with and are similarly spaced as'the shoulder portions ofthe hollow cylindrical member, the shoulder portions of the hollow member and the relatively'movable member dening the end limits of the chamber formed by surfaces of the telescoping member and comprising displacement means at each end of the chamber fordening a workingY chamber and for forming yrelief chambers consequent upon the movement of the movable member from its normal position, yieldable means in the working chamber and abutting the displacement means for positioningV normally the displacement means f against the shoulder portions of the hollow cylindrical member and the relatively movable membenfuid in said chamber for resisting movement of said movable member, openings in each of the displacement means for iluidly connecting the working chamber with the relief chambers formed consequent upon movement of the relatively movable member and for relieving fluid resistf5 4. vA two-way shock absorbing means fora coupler of aheavy transitory body comprising a hol- Asentar-io low cylindrical member, a piston member extending thereinto, one of these members being a force receiving member connected to the body, a chamber defined by surfaces of each of the members, cooperating shoulders on each of said members for defining the end limits of the chamber, displacement means in said chamber, a yieldable means for normally positioning the displacement means at each of the end limits of the chamber, fluid in said chamber for resisting movement of said piston member, openings in said displacement means for relieving fluid resistance produced upon relative movement of said piston member by the application of a force in either one of two directions, and valve means controlling the relief through the openings for completely relieving fluid resistance produced upon initial movement of said piston member by a force applied to one of the members and for gradually applying to the force receiving member the force causing relative movement of the movable member by the gradual increase of fluid resistance to the movement of the movable member until a `maximum resistance is produced, at which time the force acting on the one member is completely transferred to the force receiving member by the iiuid resistance.

5. A two-way shock absorbing means for a coupler of a heavy transitory body comprising a hollow cylindrical member connected to the body, a piston member connected to the coupler, a chamber dened by surfaces of each of the members, cooperating shoulders on each of said members for dening the end limits of the chamber, displacement means in said chamber, a yieldable means fo-r Ynormally positioning the displacement means at the end limits of the chamber, iiuid in said chamber for resisting move-- ment of said piston member, openings in said displacement means for relieving uid resistance produced upon movement of said piston member by the application of a force in either one of two directions, valve means controlling the relief through the openings for completely relieving uid resistance produced upon initial movement of said piston member by a force applied to the piston member and for gradually applying to the hollow member the force causing movement of the movable member by the gradual increase of fluid resistance to the movement of the movable member until a maximum resistance is produced, at which time the force acting on the piston member is completely transferred to the hollow member by the fluid resistance, and a further shock absorbing means comprising a chamber defined by a surface of said hollow member and a compression surface on said piston member, fluid in said chamber for resisting movement of said piston member by acting against said compression surface, and relief means for said iluid resistance for gradually reducing the relief during movement of said piston from a normal position to its position of maximum displacement.

6. A two-way shock absorber including a hollow cylindrical member and a relatively movable cylindrical member mounted therein and having a surface in spaced relation to a surface of the hollow member for defining a fluid chamber therebetween and comprising a displacement means in said fluid chamber movable in the same general direction into said iluid chamber upon relative movement of said movable members in each of said directions for resisting by fluid movement of said movable member in either of two directions of movement, by-pass means adapted and arranged to relieve fluid resistance to movement of the movable member, and Valve means cooperating with the displacement means and moved into variable restricting relation to said by-pass means by relative movement of said movable member from a normal position to a maximum displaced position and the return thereof Yfor controlling the relief of resistance through the by-pass means during movement of said member. 7. A two-way shock absorber including a hollow cylindrical member, a relatively movable member within said hollow member, longitudinally spaced supporting sections secured to said hollow member, coacting longitudinally spaced supporting sections secured to said movable member so that mounting of sai-d movable member within the hollow member defines a fluid chamber formed by surfaces and the coacting supporting sections of each of the members, and comprising displacement means at each end of the fluid chamber and movable toward and away from the supporting sections of the hollow member for resisting by fluid movement of said movable member in either of two directions of movement, yieldable means for normally positioning each of the displacement means against a coacting supporting section of each of the movable members, by-pass means for relieving the resistance to movement of said movable member, and valve means moved into variably restricting relation to said by-pass means by movement `of said movable member relative to said hollow member from a normal position to a maximum displaced position and the return thereof for contro-lling the relief of resistance through the by-pass means during .movement of said movable member.

8. A two-way shock absorber including a hollow cylindrical member, a relatively movable member within said hollow member, longitudinally spaced supporting sections secured to said hollow member, coacting longitudinally spaced supporting sections secured to said movable member so that mounting of said movable member within the hollow member defines a fluid chamber formed by surfaces and the coacting supporting sections of each of the members, and comprising displacement means normally positioned at each end of the iiuid chamber against a supporting section of the movable member, each of the displacement means being moved by a supporting section of one of the members relative to the other member upon movement of the movable member for resisting by fluid movement of said member in either of two directions of movement, by-pass means associated with each of the displacement means for relieving resistance to movement of the movable member, and valve means moved into variable restricting relation to said by-pass means by movement of said movable member from a normal position to a maximum displaced position and the return thereof for controlling the relief of resistance through the by-pass means during movement of said member.

9. A two-way shock absorber comprising a hollow cylinder and a piston member extending thereinto in spaced relation to the effective cylin-der wall for actual movement relative to the cylinder, xed shoulders on the cylinder transverse to the axis and at opposite effective ends of the cylinder, annular displacement members in the fluid space between the cylinder and piston, each of the members being movable toward and from the fixed shoulders, yielding means act- `ing on the displacement members in a manner tending to hold them against the shoulders, axially opposed shoulders on the piston member alternately engageable with the displacement members upon predetermined relative movement in opposite directions of the piston and cylinder to move them alternately away from the first mentioned shoulders, and the .displacementmembers and radially adjacent surfaces of the cylinder and piston being related in such manner that upon relative movement of the piston and cylinder in either of two directions of movement a by-pass of gradually reducing area is formed between one displacement member and the cylinder `due to movement of such displacement member by one piston shoulder and simultaneously a by-pass of gradually reducing area is formed between the other displacement member and the radially adjacent surface of the piston.

10. A two-way shock absorber comprising a hollow cylinder and a piston member extending thereinto in spaced relation to the effective cylinder wall for axial movement relative to the cylinder, xed shoulders on the cylinder transverse to the axis and opposite to the effective ends of the cylinder, annular displacement members in the uid space between the cylinder and piston, each of the displacement members being movable toward and from xed shoulders, yielding means acting on the displacement members in a manner to hold them against the shoulders, axially opposed shoulders on the piston member alternately engageable with the displacement members upon relative movement in oppositedirections betweeny the piston and cylinder to move them alternately away from the first mentioned shoulders, a valve member secured to the effective wall of the cylinder and having a variable surface in operative relation with each of the displacement members for alternately forming a by-pass of'gradually reducing area by movement of one of the displacement members, and a valve member secured to the piston member and having a variable surface in operative relation with each of the displacement members for alternately forming a bypass of gradually reducing area by movement of one of the displacement members.

11. A two-way shock absorber including ahollow cylindrical member and a relatively movable cylindrical member mounted therein and having a surface in spaced relation to a surface of the hollow member for dening a fluid chamber therebetween and comprising a displacement means in said fluid chamber for resisting by iluid movement of said movable member in either of two directions of movement, b-y-pass means adapted and arranged to relieve fluid resistance to movement of the movable member, valve means moved into variable restricting relation to said by-pass means by movement of said movable member from a normal position to a maximum displaced position and the return thereof forv controlling the relief of resistance through the bypass means during movement of said member, and a secondary shock absorber means comprising a fluid chamber defined by surfaces of said hollow member, said relatively movable member extending thereinto, fluid in said chamber for resisting movement of said relatively movable member, means for relieving resistance to movement, and means controlling said relief means for gradually reducing the relief of resistance to movement during movement of said relatively movable member from a normal position to a maximum displaced position. y

' HANS JOHANSEN. 

